Demolition mill

ABSTRACT

A demolition mill for solid debris utilizes free swinging demolition hammers rotatably mounted on shafts interconnecting solid metal wheels journaled in a housing. The hammers extend radially of the wheels under the action of centrifugal force to break, shatter or pulverize all kinds of solid debris. A hydraulic feed rotor is journalled adjacent the housing inlet and includes a cylindrical feed roller driven by a hydraulic motor mounted in a tube positioned within the roller. Lengths of chain or serrated bars welded to the periphery of the roller assist in feeding material to the hammers.

United States Patent [191 1111 3,826,437 Warren, Jr. et al. 1 July 30,1974 DEMOLITION MILL Primary ExaminerRoy Lake [75] Inventors: Fred E.Warren, .lr., Tigard; Asst-am Examiner-E F.Desmond Kenneth F. Fling,Sherwood; Gary Attorney, Agent, or Fzrm-Klarqutst, Sparkman,

R. Moore, Hillsboro, all of Oreg. Campbell Leigh & Whinston [73]Assignee: Ecolo-Tech, Inc., Sherwood, Oreg.

22 Pl d F b l [57] ABSTRACT 1 l e e 1973 A demolition mill for soliddebris utilizes free swinging PP 333,401 demolition hammers rotatablymounted on shafts interconnecting solid metal wheels journaled in ahous- 152 11s. c1 241/186 R, 241/101.7, 241/195 hammersfaxtend radiallythe wheels under [51 1m. (:1. B02 13/04 the cemnfuga force break Shatter[581 Field of Search 241/185 R 186 R 101 M verize all kinds of soliddebris. A hydraulic feed rotor 241/101 7 i is journalled adjacent thehousing inlet and includes a cylindrical feed roller driven by ahydraulic motor [56] References Cited Lengths of chain or serrated barswelded to the pe- UNITED STATES PATENTS riphery of the roller assist infeeding material to the 1,266,894 5/1918 Williams 241/195 hammers,3,482,788 12/1969 Newcll 24l/l94 X 5 Claims, 8 Drawing Figures mountedin a tube positioned within the roller.

1 DEMOLITION MILL BACKGROUND OF THE DISCLOSURE This invention relates todemolition and disposal machines for breaking, shattering andpulverizing solid waste debris.

With environmental clean-up rules becoming increasingly restrictive, aversatile and tough, all-purpose demolition and disposal machine forbreaking, shattering or pulverizing solid waste material has become anecessity.

Such a machine to be successful must be capable of handling all types ofmaterial, such as bark, green wood, seasoned timber with nails, and theproducts of building demolition including such diverse items as conduit,junction boxes, metal gutters, roofing and such problem materials asglass, brick and plasterboard. Additionally, such, a machine must becapable of disposing of brush, root mass with sod and stones, as well asthe byproducts and debris from logging operations.

Reduction in size of waste materials such as the above leads to theirmost efficient disposal since such material can then be recycled or usedas ground cover, fill or for erosion control. If waste material ispulverized fine enough, it can be distributed by conventional roadsidespreading methods.

Accordingly, it is the primary object of the present invention toprovide a demolition and disposal machine for breaking, shattering orpulverizing all types of solid waste and debris.

It is a further object of the present invention to provide such anapparatus that will be tough and rugged and which can quickly reduce thesize of material of the type heretofore described without damage toitself.

It is a still further object of the present invention to provide such anapparatus that can produce an end product of a size to suit the desiresor needs of the operator.

It is a still further object of the present invention to provide such anapparatus that can operate at a rate commensurate with a crew s abilityto feed it.

SUMMARY OF THE INVENTION The disposal machine of the present inventioncomprises a housing defining an inlet throat and an outlet, and ademolition rotor journaled in the housing on a generally horizontal axisextending in a direction transversely of the throat.

The demolition rotor comprises at least two wheels mounted for rotationabout the axis and a plurality of circumferentially uniformly spacedshafts interconnecting the wheels adjacent the peripheries thereof, theshafts being adapted to revolve with the wheels about the axis.

A plurality of free swinging demolition hammers are rotatably mounted oneach of the shafts. The hammers extend radially of the wheels under theaction of centrifugal force when the wheels rotate about the rotor axisfor striking contact with material fed into the housing inlet. Thehammers hang vertically from the shafts when the rotor is at rest.

Means are provided operatively to connect the rotor with a source ofpower for rotating the rotor at a speed sufficient to cause the hammersto demolish the material fed into the housing.

The hammers are mounted on the shafts in a manner such that the hammerson one shaft interleave with those mounted on an adjacent shaft when thewheels are at rest, thereby to avoid interference with each other. Thespacing of the hammers, however, is such as completely to cover theentire lateral distance between the wheels, thus insuring contact withevery bit of material fed into the rotor.

The hammers themselves are free swinging, 360 rotatable plates havingtheir longitudinal axes disposed radially of the wheels when the latterare rotating. A hammer plate is attached to a shaft by means of anaperture positioned at one end of the plate, the other end of the platebeing symmetrically curved concavely inwardly. The sides of each plateare also symmetrically curved concavely inwardly, so that each of thesides forms an acute angle cutting corner with the end of the plate.When such cutting corners become worn after extended use, reversal ofthe entire rotor assembly places the opposite cutting corners instriking position. Subsequent erosion of the ends of the plates resultsin a regeneration of the initial end curvature, thereby to achieve aself-sharpening of the hammers.

A feed rotor journalled adjacent the inlet throat provides braking andregulated control over material fed to the demolition rotor. The feedrotor comprises a generally symmetrical feed roller, and motor receivingmeans disposed within the roller and connected to the apparatus frame.Hydraulic motor means mounted in the receiving means drivingly connectsto the feed roller, which rotates on bearing means mounted on the motorreceiving means. Means attached to the outer peripheral surface of thefeed roller assist in feeding material to be demolished into the inletthroat.

BRIEF DESCRIPTION OF THE DRAWINGS on line 55 of FIG. I and illustratingthe construction of the feed rotor of the present invention.

FIG. 6 is a sectional view taken on line 6-6 of FIG. 5.

FIG. 7 is a side view of a portion of a feed roller illustrating analternate embodiment of feeding means attached to the outer peripheralsurface thereof.

FIG. 8 is a sectional view taken on line 8-8 of FIG. 7.

DESCRIPTION OF THE PREFERRED EMBODIMENT Referring to the drawings, thedemolition mill 10 of the present invention includes a heavy duty2-wheel trailer frame 11 having high flotation tires 12 on adjustableside mounted stub axles 13. A front draw bar 14 is provided for towing.A diesel engine 15 providing or more B.H.P. and mounted on the frame 1]drives a demolition rotor 16 journalled in a housing 17 through 3 apower takeoff 18 and a belt drive 20. The engine also furnishes powerthrough an auxiliary belt drive 21 to a hydraulic pump (not shown)located in a gallon hydraulic reservoir 22 mounted behind the engine 15on the frame 11.

Hydraulic lines 23 with appropriate directional control valves carryhydraulic fluid under pressure from the reservoir 22 to a hydraulicmotor 24 for a feed rotor 25 positioned rearwardly of the demolitionrotor 16 and to another hydraulic motor 26 which drives a belt conveyor27 positioned on the bottom 28 of a rearwardly disposed foldable feedhopper 30. Broken, shattered and pulverized debris from an outlet 31 inthe housing 17 is carried through an exhaust chute 32 mounted onsupports 33 forwardly of the apparatus to a point of disposal.

A feature of the invention resides in the demolition rotor 16 which isillustrated in greater detail in FIGS. 3 and 4. Three one-half inchthick solid circular steel 20 inch diameter end plates or wheels 34having hubs 34a and mounted 9 inches apart are keyed for rotation with ahorizontal center shaft 35 journalled in bearings 36 on opposite sidesof the housing 17. Each wheel 34 has, in the apparatus shown, ninedrilled and induction hardened holes 37 circumferentially uniformlyspaced adjacent the periphery 38 thereof. A 1.25 inch diameter steelcutter shaft 39 preferably made of 4,140 steel fully hardened toRc'50/55 is received in a machinefit in each set of opposed holes 37 tointerconnect adjacent wheels 34. Shafts 39 thus revolve with the rotor16. about its horizontal axis 40.

The housing 17 is preferably made of 5/8 inch thick Tl (armor) plate toprovide suitable protection against the hazards of breaking hammers anddemolished material. Horizontal plates 42 and 43 welded to thecylindrical portion 44 of housing 17 providean inlet 45 having a crosssection 12 by l8 inches in size and which is positioned such that itsupper surface 46 is coplanar with the horizontal radial plane 47 throughthe axis 40, the lower surface 48 of the inlet 46 being slightly abovethe lower horizontal tangent to the cylindrical portion 44. The outlet31 is formed by an upper plate 50 and a lower plate 51 welded to theopposite or downstream side of the portion 44 at a location generallyopposed to that of the inlet 45, and 'the entire housing assembly isbolted to the frame 11 through elongated slots (not shown) to providelongitudinal adjustability as required.

A plurality of free swinging, 360 rotatable demolition hammers 52 arerotatably mounted on each of the nine shafts 39 such that the hammerscan extend radially of the wheels 34 under the action of centrifugalforce when the wheels rotate. In the embodiment illustrated, six suchhammers 52 are positioned on each shaft 39 between adjacent wheels 34,i.e., a total of 12 hammers on each of the nine shafts 39. Spacers 53are provided in between each hammer and the hammers are spaced on theshafts 39 ina manner such that the hammers mounted on one shaftinterleave with the hammers mounted on an adjacent shaft when the rotoris stationary and the hangers are hanging vertically from the shafts,thereby to avoid interference with each other. The spacing of thehammers on the shafts, however, is such as completely to cover theentire distance between adjacent wheels 34 so that at least one hammerwill contact each piece of material irrespective of its lateral positionwith respect to the wheels 34 as long as the material is within strikingrange of the hammers.

A preferred hammer spacing pattern is illustrated in FIG. 4, wherein thewheels 34 have a diameter of 20 inches and are positioned 9 inchesapart. For convenience the nine shafts 39 are identified by numerals39a-39i, inclusively; the three wheels by numerals 34a-34c, inclusively.

In the example shown the first shaft 39a rotatably supports six suchhammers 52 between the wheels 34, the innermost ones being immediatelyadjacent the center wheel 34b. On the next adjacent shaft 39b thehammers are positioned such that there is equal spacing as between theoutermost hammers and the adjacent wheels. On the next shaft 39c thehammers are spaced such that the outermost ones are adjacent the outerwheels 34a and 340.

The hammers are mounted on shaft 39d such that the innermost ones occupyan intermediate position as respects those on shaft 39b. The hammers aremounted on shaft 39e in a manner which is a mirror image of those onshaft 39d. The hammers are mounted on shaft 39f with slightly less spacebetween the position of the innermost hammer than is present in shaft39d. The position of the hammers on shaft 393 is such as to provideslightly more space inboard of the innermost hammer than is present onshaft 39b. The position of the hammers on shaft 39h is the same as onshaft 39a and the position of the hammers on shaft 39i is the same as itis on shaft 39b.

Other spacing patterns are, of course, possible, the only requirementsbeing the necessity to avoid interference when the rotor 16 is at restand the further necessity to .cover the entire distance between thewheels 34 to insure striking contact throughout the entire zone.

Each of the hammers 52 comprises a cutting tooth 54 formed from agenerally rectangular fully hardened piece of 4,]40 or 4,340 steel platepreferably 6 inches by 2% inches by 0.375 inch thick. The teeth arepreferably fully hardened in a salt bath to Re 50/55. Each tooth isprovided with an aperture 55 adjacent one end 56 for receiving one ofthe shafts 39, the aperture 55 being located on the longitudinal centerline or axis 57 of the tooth. As will be understood, the center line 57is disposed radially of the wheels 34 when the latter rotate.

The opposite end 58 of each tooth is cut in the form of a symmetricalinwardly-concave curve at a preferred radius of 3.25 inches. The sides60 of the tooth are similarly symmetrically and inwardly-concavelycurved on identical 3.25 inch radii. The sides 60 and the end 58 of atooth thus form on each side a relatively sharp cutting corner 61 havingthe acute angle shown.

We have found that the clearance between the housing 17 and the hammers52 is not critical inasmuch as the hammers do not operate by cutting thematerial, but rather operate on a ballistic principle, the teeth 54 justshattering the material as they come in contact therewith. Also, sincethe hammers 52 are freely rotatable on the shafts 39, the support forthe rotor 16 can be less rigid than otherwise, making it possible tojournal the rotor in the housing 17 as we have described.

Operation of the rotor 16 unavoidably causes wear on the strikingcorners 61 of the teeth 54, which wear ultimately causes them to becomeround. We have discovered, however, that if the entire rotor 16 bereversed in the housing 17 such that operation of the apparatus bringsthe opposite cutting corners of the hammers into striking position, thewiping effect of material, as it passes along the ends 58 of the teethas the material is being demolished, causes a totally unexpectedsharpening of the previously dulled or rounded opposite strikingcorners. This wiping effect causes a regeneration of the original endcurvature as the teeth wear down in length, thereby resulting in aneffective resharpening of the acute angle cutting corners on theopposite and theretofore dull sides. We have found that the pulverizingof concrete is particularly effective in resharpening of the teeth dueto the erosion caused by the wiping action of the material on the ends58. We have been able to operate for as long as 3,000 hours on a givenset of teeth.

With 108 hammers working in the rotor (12 hammers on each of nineshafts), normal operation provides 237,000 striking contacts per minutewith in excess of 2,000 pounds of force per strike. This has beendemonstrated to be sufficient to break up 5 inch wide by 5/8 inch thickmild steel plate with no appreciable damage to the hammers.

When demolishing building debris, the rotor can handle up to andincluding inch water pipe, junction boxes, metal gutters and similaritems. Glass, brick, plasterboard and even rock can be pulverized. Otheritems that can be handled by the rotor are seasoned timbers with spikes,conduit, door knobs, roofing debris and drain gutters, green and roundwood, brush as well as root mass with sod and stones, slab barkincluding both redwood and cedar bark, paper and cardboard scrap, tincans, bottles, wet garbage, composition materials, and insulatingremnants. The force of the rotation eliminates the necessity of ablower, although such could be incorporated if desired, the pulverizeddebris being discharged merely by the operation of the rotor 16 throughthe exhaust chute 32.

A further feature of the invention resides in the feeding apparatus. Thefoldable hopper 30 has a bottom 28 and outwardly flaring sides 64 and isdisposed rear wardly of the rotor 16 and housing 17. The hopper 30 isprovided with a belt conveyor 27 supported on end rollers 65 and drivenby the hydraulic motor 26 which is powered by hydraulic fluid underpressure from the reservoir 22 and operated by suitable controls 66. Thefoldable nature of the hopper facilitates transportation of theapparatus.

A pair of generally L-shaped arms 67 are pivotally attached to thehousing 17 on each side thereof immediately adjacent wear plates 68positioned at the top, each of the arms 67 being vertically movable bymeans of a hydraulic cylinder 70 and piston 71 mounted on the frame 11and pivotally attached to the arm 67 by a clevis 72. The feed rotor 25is supported by the arms 67 adjacent the inlet 45 for rotation on anaxis 73 parallel to the axis 40 of the demolition rotor 16, such thatextension of the pistons 71 causes the arms 67 to lift the rotor 25should such be desired.

As shown in FIGS. 5 and 6, the rotor 25 includes a I cylindrical feedroller 75 having an end plate 76 fitted with a stub shaft 77 forrotation in a bearing 78 mounted on one of the arms 67a. The roller 75is provided with an intermediate web 80 having a centrally located hub81 welded thereto and an additional annular web 82 welded adjacent itsopposite end 83 for a purpose hereinafter to be described.

The hydraulic motor 24 serviced by the hydraulic lines 23 from thereservoir 22 is positioned in a motor tube 84 which is positionedinteriorly of the roller 75, the tube 84 having an access opening 85 atthe top thereof, the motor 24 being attached to an end wall 86 of thetube 84 by bolts 87 and having a drive shaft 88 connected to the hub 81by a key 90. A bearing flange 91 welded to the outer end 92 of the motortube 84 has a cylindrical extension 93 threaded at its end 93a and whichextends outwardly of the roller 75 through the annular web 82.,Theextension 93 has a central bore 93b to accommodate the lines 23 andsupports a bearing 94, the outer race 95 of which is keyed to a bearingring 96 attached to the web 82 by bolts 97. A locking collar 98 isreceived on the extension 93 being retained by a set screw 100, theextension 93 being locked to the arm 67b by a key 101 and the entireassembly being retained by spanner nuts 102 and a lock washer 103 asshown. Hydraulic power to the motor 24 causes rotation of the driveshaft 88 and consequent rotation of the feed roller 75 in the bearing 78and about the inner race 104 of the bearing 94 at the other end 83, theassembly providing for efficient placement of the hydraulic motor 24 yetready access thereto by means of the opening 85 in the tube 84. I

In operation the feed rotor 25 actually functions as a brake, floatingon the debris fed into the hopper 30 by pivotal action of the arms 67.The feed rotor 25 and the conveyor 27 are operated in series to regulatecontrol over the rate at which material is fed into the demolition rotor16, thereby to permit the production of various sized end products tosuit the desires or needs of the operator. Adjusting the speed of theconveyor 27 and the rotational speed of the roller 75 also permits theapparatus to operate at a rate suited to the crews ability to feedmaterial to it.

Means in the form of chains 106 welded to the outer peripheral surface107 of the feed roller 75 at circumferentially spaced intervalstherearound assist in the feeding of material into the inlet throat 45.The chains 106 are a desirable feeding means for garbage and generalrefuse.

As shown in FIGS. 7 and 8, alternatively the feeding means can take theform of serrated bars 108 welded to the outer peripheral surface 107a ofa roller 75a at circumferentially spaced intervals therearound, the bars108 having their ends 109 bent at an angle to the elements 110 of thecylindrical surface 107a as shown. The serrated or toothed constructionis desirable for disposal of material such as railroad ties and woodhaving loose bark.

Utilizing hydraulic power for the feed roller 75 and the conveyor 27makes it possible to extend the use of the apparatus to a variety ofauxiliary tools such as hydraulic saws which can be coupled to thehydraulic system as desired. The hydraulic system also makes it possibleto incorporate an emergency safety stop system.

We claim:

1. In a demolition mill having frame means, housing means mounted onsaid frame means and defining an inlet throat and an outlet, ademolition rotor journalled in said housing means on a first generallyhorizontal axis extending in a direction transversely of said throat, aplurality of hammer elements carried by said rotor for demolishingmaterial fed into said inlet throat, means for imparting rotation tosaid demolition rotor and a source of hydraulic fluid under pressure,

a feed rotor journalled adjacent said inlet throat on an axis parallelto said first axis, said feed rotor comprising a generally cylindricalfeed roller, motor receiving means disposed within said feed roller andconnected to said frame means,

hydraulic motor means mounted in said motor receiving means anddrivingly connected to said feed roller,

means connecting said hydraulic motor means to said source of hydraulicfluid,

bearing means mounted on said motor receiving means, said feed rollerbeing adapted to rotate on said bearing means, and means attached to theouter peripheral surface of said feed roller for feeding material intosaid inlet throat.

2. The feed rotor of claim 1 further comprising a pair of arm meanspivotally connected to said housing means and extending on oppositesides of said feed roller,

said motor receiving means being attached at one end to one of said pairof arm means,

said bearing means being mounted on said motor receiving means at saidone end thereof, said feed roller rotation on said bearing means at oneend of said feed roller,

said feed roller being journalled at its other end in the other of saidpair of arm means.

3. The feed roller of claim 2 further comprising web means disposedwithin said feed roller, said hydraulic motor means being drivinglyattached to said web means adjacent the other end of said motorreceiving means.

4. The feed rotor of claim 1 in which said feeding means comprise chainmeans.

5. The feed rotor of claim 1 in which said feeding means compriseserrated means.

1. In a demolition mill having frame means, housing means mounted onsaid frame means and defining an inlet throat and an outlet, ademolition rotor journalled in said housing means on a first generallyhorizontal axis extending in a direction transversely of said throat, aplurality of hammer elements carried by said rotor for demolishingmaterial fed into said inlet throat, means for imparting rotation tosaid demolition rotor and a source of hydraulic fluid under pressure, afeed rotor journalled adjacent said inlet throat on an axis parallel tosaid first axis, said feed rotor comprising a generally cylindrical feedroller, motor receiving means disposed within said feed roller andconnected to said frame means, hydraulic motor means mounted in saidmotor receiving means and drivingly connected to said feed roller, meansconnecting said hydraulic motor means to said source of hydraulic fluid,bearing means mounted on said motor receiving means, said feed rollerbeing adapted to rotate on said bearing means, and means attached to theouter peripheral surface of said feed roller for feeding material intosaid inlet throat.
 2. The feed rotor of claim 1 further comprising apair of arm means pivotally connected to said housing means andextending on opposite sides of said feed roller, said motor receivingmeans being attached at one end to one of said pair of arm means, saidbearing means being mounted on said motor receiving means at said oneend thereof, said feed roller rotation on said bearing means at one endof said feed roller, said feed roller being journalled at its other endin the other of said pair of arm means.
 3. The feed roller of claim 2further comprising web means disposed within said feed roller, saidhydraulic motor means being drivingly attached to said web meansadjacent the other end of said motor receiving means.
 4. The feed rotorof claim 1 in which said feeding means comprise chain means.
 5. The feedrotor of claim 1 in which said feeding means comprise serrated means.